Shoe tacking machine



6v Sheets-Sheet l W. GLEISSNER SHOE TACKING MACHINE Filed Sept. 23, 1940Nov. 14, 1944.

Nov. 14, 1944.

W. GLEISSNER SHOE TACKING MACHINE 4 Filed s'ept. 25, 1940 6 Sheets-Sheet3 NOV' 14, 1944- w. GLElssNER SHOE TACKING MACHINE Filed Sept. 25, 19406 Sheets-Sheet 4 Nov. 14, 1944. w. GLEISSNER SHOE TACKING MACHINE Filedsept. 2s. 1940 1g. 5a M Eig. 6

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NOV. 14, 1944. w GLEISSNER 2,362,480

' sHoE 'TACKING MACHINE Filed sept. 25, 1940 e 4sheets-sheet evGMS/argv' fected at equal distances from the ed Patented Nov. 14, 1944UNITED STAT ES .PATE-N astri- T OFFICE SHOE TACKING MACHINE WalterGleiss'ner, Weissenfels-Saale, Germany;

vested in the Alien Property Custodian Application September 23, 1940,Serial No.

. In Germany July 7, 1939 4,23 Claims Machines .are known for makingshoes, particularly tacking machines. VWith these known.

applicable in the case of' tacking machinesequipped with a punchingdevice.

f- This invention relates to'a shoe tacking machine and moreparticularly to means to mechanically and automatically. oscillate thelshoe support or work holder of such a machine relatively to the tackingand punching tools.

The invention resides in the provision ofan" oscillatory shaft connectedwith the shoe support or work holder, which oscillatory shaft is powerrotated .alternately in one direction and then in the other directionfrom land to its normal position, to present the work, as a shoe tip, tothe tools in such manner that the tacking and punching operations,Acommencing at the tip of the toe of the shoe, are first eiected fromsaid tip along one side of the toe of the shoe, the operation of thetools being arrested after the ed upon, and the power disconnected fromthe oscillatory shaft. Other power means rendered effective incident tothe preceding operation, restores the oscillatory shaft to its startingposimeans is rendered effective to rock the oscillatory shaft in theopposite direction to present the opposite side of the toe of the shoeto the tools, after which this power means is automaticallyvdisconnected from the oscillatoryshaftfto enable said other power meansto restore the oscillatory shaft and work to their Vstarting positions.

The invention renders possible the tacking of the front of the shoe,commencing at the tip by a single series of automatically effectedoperations with simultaneous punching.

As a result, damage to the goods usuallyoccurring when the work ismanually presented t'o the tools, is avoided, the work of the operatoris relieved, and apart from proper stretching ofthe leather or othermedium, the punching is efge` of the shoe. Furthermore, the spacingbetween the punched holes is approximately equal depending upon theparticular adjustment o f .the controls for the work support, theworking of the leather onto the'edge of the last, the punching, and the`work shifting being more readily an desired extent of the shoe tip hasbeen operat- .g5-v

, 30 tion, incident to which the rst-named power d accurately performedthan heretofore. e

The invention comprises a work holder oscillating mechanism, withcontrol means 'to intermittently connect the oscillating mechanism witha power drive, to enable the power drive to advance'the work holderrelatively to theworking tools, first in one direction from anintermediate starting position and then in the other direction, meansvas auxiliary'motors being provided to restore the workv holder to itsstartingA position after each advance. The control means isintermittently.operatedwto set means to contro1 the direction `andextent of advance imparted by the power drive to the vwork holder;- tocontrol the engagement and disengagement oi the power 'and ythe workholder, and to determine the time of operation of the work holderrestoring means. y The connection of the control means with the powerdrive mechanism, after-starting the machine for operation, is, in turn,lrendered effective under control of the ywork holder oscillating means.1 i

The control mechanism isv rendered by the power drive mechanism at theconclusion ofA each advance of the work holder from its startingposition, and by the auxiliary -1 motor during the rst returnv stroke ofthe work holder.

Means to vary the extent of each advance stroke and rto temporarilydetain thework holder in its advanced position also forms part of theinvention, as doesthe means to yieldingly maintain the work in contactwith the during the oscillations of the work.

`Geueral description y The machine of my invention is intended t0function as follows:

The work, as a shoe, is securd'in a suitable,l rotatable holder' or shoesupport which, in turn, is pivotally connected to the frame of themachine for movement towards and from an edge rest, vtheposition ofwhich rest determines the distance from the outer edge of the shoe soleat which the punching and tacking line shall be located.

The shoe is applied to the work holder or support when the latter is inits idle position. 5,0y remote from the ed ge rest, after which the op-,erator manually rocks the work support to bring the lshoe into contactwith the-edge rest. I n' After the shoe support is properly positioned,and means is adjusted to select the sequence of directions in which theshoe is to be presented to effective Y edge rest the tools, the operatoractuates a pedal to connect the power with the operation-controllingparts of the machine.

One of the first functions performed by the operated mechanism is torender effective av means to yieldingly retain the work support inposition to press the work against the edge rest, thereby relieving theoperator of this labor and placing the entire control of the work on themachine.

coincidentally, means is rendered effective for partially rotating thework support in the selected direction through bevel gearing to traversethe shoe from the point of the toe, part way along the side, duringwhich traverse the punching and tacking operations are eifected.

Provision is made to vary the extent of this traverse, to adapt themachine for shoes of varying sizes.

Upon the completion of the predetermined traverse of the shoe inthe rstdirection selected relatively to the punching and tacking mechanism, thepoweris automatically disconnected from the machine, and later, a springwhich has been tensioned by the machine incidentto the traverse of thework in the rst direction, operates *to ,return the work support andwork to its initial working or starting position.

Means operableincident tov the return of the Work support to itsstarting position reconnects the power with the operation-controllingmeans, whereupon the work support is rocked in the opposite directionfrom its initial working or starting position to which it wasautomatically returned by spring action, and at the conclusion of thetraverse of the shoe in said opposite direction, the power is againautomatically disconnected, after which a second spring tensioned by themachine in traversing the shoe in said last-named direction. againreturns the work support and work tov initial working position.

Incidental to such second return to initial working position. the meansfor holding the work supportv to yieldingly press the shoe againstl theedge rest is released. so that the work support may rock away from theedge rest to enable the shoe to be removed and another substituted.

It will be understood that the punching and tacking mechanisms operateon the shoe during the traverse of the shoe from its point or toe ineither direction, and are idle during each return of the shoe to itsinitial workingor starting position. Y

In addition to the inventive features embodied in the means forautomatically effecting the traverse of the work from and back to itsinitial working or starting position. in opposite directions, theinvention includes novel means to automatically eifect the reversal oitraverse of the work, as a shoe. novel means to prevent overthrow of thework holder and work in either direction of movement. novel means toinsure the proper oscillation of the work holder in either direction.and novel means to effect and control the yielding contact of the workagainst the edge rest.

[n order to eifect the traverse of the work in one direction from thepoint of the toe for a predetermined distance relatively to the punchingand tacking mechanisms, and the returnA of the work to initial workingposition, followed by a traverse of the work relatively to the punchingand tacking mechanisms in the opposite di rection and return, there isprovided a coupling or gear driven from the same shaft which impartsoscillating motion to the work support.

Power for oscillating the shaft for communieating oscillatory motion tothe work support is supplied from the counter-shaft of the machine,through a reversible link drive, the sequence of the alternatingoscillations being controlled by a cam on the control shaft.

The connection of the power to the countershaft is controlled by linkageoperable by hand or foot power, which enables the operator to arrest themachine at will, whereby to interrupt the' punching and taskingoperations at any time.

One embodiment of the invention is illustrated in the accompanyingdrawings, in which Fig. l is a side elevation, partly in section, of ashoe tip punching and tacking machine of conventional type, to which theinvention is vapplied,

Fig. 2 is a diagrammatic view in vertical section through Fig. l, online 2'Z looking towards the right illustrating the drive and thecontrols for imparting oscillating movements alternately in oppositedirections, each oscillating movement traversing the work from andreturning it to its initial working position.

Fig. 2a is a similar view showing the parts in their normal idlepositions,

Fig. 3 is a diagrammatic view in vertical section through Fig. 1, online 3-3, looking towards the right, illustrating the pedal mechanismand the automatic controls for connecting the power with the controlshaft,

Fig. 4 is a diagrammatic illustration of the link motion for impartingmovement to the work support,

Fig. 5 is a fragmentary view in side elevation showing the link motionand its connection with the work traversing disk, and the centeringmechanism to return the disk-driving pawl carrier to .its normalpositiom Fig. 5a, is an edge View, partly in section, of

,the reversible, intermittent feed, and centering section, showing theidle position of the means for retaining the link motion and theoscillatory shaft, at one limit of their movement,

Figure 7a is a .fragmentary sectional view through the brake member andfriction disc of Figure 7, l

Fig. 8 is a view similar to Figure '7 but showing the parts in their`effective positions,

Fig. 9a is a graph showing an alternating oscillatory path illustratingthe movement of the shoe from the point of the toe, first to the left,then back to initial position, and thence to the right and backv toinitial position, the return paths being indicated by broken lines ineach instance, and

The shoe or work |is applied to, and held f' in place on the worksupport by suitable clamping means, and after the work is clamped to thework support, the latter is manually rocked until the tip or toe of theshoe contacts the' edge rest 31, as shown in Fig. 1.

Contact of the shoe with-the edge rest is automatically maintainedduring the operation of the punching and tacking mechanisms, not shown,on the work, in a manner hereinafter explained.

A suitably supported, normally idle counterqualified by (2) anadjustable means fon. determining the direction of such rocking eitherto rightl or to left of the initial position of the work support andwork relatively to the edge rest, and (3) means to determine the extentof 4 such rocking.

shaft 33 supports a continuously-operated drive.

pulley 39 journaled thereon.

A second pulley 40 (Figs. 1 and 3) rigidly connected with the drivepulley 39 loose on the 1j counter-shaft 33 of the tool head, isconnected by a belt 3| with a driven pulley 4| journaled on a pintle 42projecting from the machine frame, thedriven pulley 4| being attached toone member 43 of a normally idle one-revolution coupling 43, 44 likewisejournaled on the pintle 42.

The pulleys 40 and 4|, and the driving memvber 43 of the couplingcontinuously rotate in one direction even when the machine and its a.

counter-shaft 33 are not in operation.

The driven member 44 of the coupling has fastened thereto a drive pinion45 in constant mesh with a driven gear 46 fast on a control shaft 41,the diameter of the gear 46 being, in

this instance, four times greater than the diameter of the drivingpinion 45.

The horizontal control shaft 41 is suitably journaled in the machinehead frame |3, the driven gear 46 being fast on one end of the shaft.Near its opposite end, the shaft also supports a peripherally groovedcam wheel 48 for controlling the means which automatically `presses thework against the edge rest 31 as hereinafter explained.V K i A sleeve 32splined on the control shaft 41 l for axial adjustment along the shaftbut rotating therewith, supports a pair of complementary control cammembers 49, 50 spaced apart from one another.

Cam grooves 49' and 50' in the apposed faces of the respective cams 49and 50 have the dual purposes of controlling the direction ofoscillation of the work support 3 relatively to the edge rest 31, and ofcontrolling the application of power to rock the work support 3 and thework on the advance stroke in either directionfrom. the

-neutral intermediate or initial position of, the

`work support relatively to the edge rest, and

after thek work holder and work have completed their advance in eitherdirection, the control ,cams permit a supplementary motive power torestore the work holder and work to their said initial positions.

' A better understanding of this :part of the invention will be had ifit is borne in mind that there is provided (l) an intermittently drivenpower -means to rock or advance the work support and work relatively tothe edge rest, the

operation of which power means is modied or 7 l cessive areas to thetools.

'stroke without affecting the adjustment of the meansffor determiningthe extent or the direction of such stroke, and upon the disconnection,

of the poWer, other means returns thework support and work to itsinitial position relatively to the edge-rest.

Work support traversing mechanism The shaft 4 (Figi 1) of the rockingwork support '3 is connected by bevel gears 5 with an oscillatory driveshaft 2| n suitably journaled in bearings in the head frame I3.

A friction disk 12 (Figs. 1, 2 and 4 to 6 inclusive) fast on theoscillatory shaft 2|, which disk maybe peripherally grooved, as shown,is advanced or partially rotated in one direction or the other by powerapplied thereto by a pawlcarrier'13 anddouble-acting friction pawl 15,to rotate the shaft 2|, the work support 3 `and the work'relatively tothe edge rest to present suc- A gear |05 fast on the oscillatoryshaft`2| is in constant mesh with a second gear |06 fast on arestoringshaft |01 journaled in the head frame I3 parallel with theoscillatory shaft. Depending upon the direction of the advance impartedto the oscillatory shaft 2|, one or another of two opposed-springmotorsv ||0, isl

tensioned by the rotation transmitted to the restoring shaft |01 by theoscillatory shaft 2|.

At the conclusion of the effective stroke of the pawl carrier 13 and itsdouble-acting pawl 15, and consequently at the end of the advancerotation imparted thereby to the oscillatory shaft 2|, the supply ofpower to the pawl carrier and pawl is automatically interrupted.

To avoid interference with other mechanisms, as Well as'to maintain asystematic cycle of operations, each depending upon the precedingoperation, means is provided to retain the tensioned work supportrestoring spring I0 or potentially effective until other Amechanismshave operated, after which thetensioned spring motor ||0 or as the casemay be, becomes effective to reversely rotate the .restoring shaft |01and throughgears |06, |05, the oscillatory shaft 2|, back to .theirstarting or initial positions to return the work support and work backto their initial positions.

Means 10 (Figs. 5 and) tensioned by the pawl carrier 13 on its power o radvancing stroke, acts 'to center the pawl carrier and pawl in theirstarting positions upon the return ofthe pawl carrier to itsnormalposition tively shiftable manually into and out of oper-jy ativeposition.

vThese conditioning cams'also control the operativity of the driving cammember 69, and preprior to the dis-v vent premature operation. of thespring motors H0, which return the oscillatory shaft 2|, work support 3and the work to their initial positions.

' It will be recalled that there is a normally idle one-revolutionclutch mechanism 43, 44 between the constantly rotating driven pulley 4|and the driving pinion 45 inmesh with the driven gear which is fourtimes the size of the driving pinion.

A clutch control lever |32 (Figs. l and 3) normally holds' the clutchcoupling 43, 44 disconnected.

After the work support 3 has been manually rocked to bring the top ortoe of the shoe against the edge rest 31, the operator steps on the end|28w (Fig. 3) of the pedal lever |28 pivoted at |2821 to depress thepedal clockwise against the tension of its return spring |28c. The freerear end of the pedal lever normally engages beneath a yielding by-passpawl |29 pivotedY at the forward end of an intermediate lever |30rocking about the pin |30a, the rear end of which lever is connected bya rod |31 with one arm of the'gear clutch controllever |32 pivoted at|32a.

A spring |3017 conveniently connected'to the intermediate lever |30,tends to rock the intermediate lever clockwise and through the ro'd |3|,normally restores the gear clutch control lever |32 to position toeffect the disengagement of the one revolution clutch members 43, 44 andto hold them disengaged.

Therefore, when the pedal lever |28 is rocked clockwise, its rear endrocks the intermediate lever |30 clockwise against the tension of itsrestoring spring |3017, to shift the gear clutch control lever |32 toits ineffective position, after which the rear end of the pedal lever|28 escapes past the by-pass pawl |29, thereby releasing the gear clutchcontrol lever |32 and the intermediate lever |30 to the action of therestoring spring |3017 which returns both levers to their normalpositions, irrespective of the position of the pedal lever |28.

Return of the gear clutch control lever |32 is without effect on theinstant rotation of the pinion 45 because the clutch members 43, 44 havebeen rotated past the end of the clutch control lever |32, which remainsin position to automatically disconnect the clutch members 43, 44 at theend of a single rotation of the pinion 45, the pinion in its rotationadvancing the vdriven gear `48 a quarter of a revolution.

1 Upon release of the pedal lever |28, its spring |280 restores thepedal counter-clockwise to its normal position, the rear free end of thepedal lever wiping idly past the Aicy-pass pawl l|29 to position its`rear end beneath the by-pass pawl.

The large driven gear 46 being fast on the control shaft 41'turns the'latter one quarter of a revolution, and the complementary control cams49, 50 axially but not rotatably shiftable on the control shaft arelikewise rotated one quarter of a revolution.

Control mechanism jecting from the head frame I3, the arm 54 eX- tendingupwardly to a, point between the apposed cam-grooved faces of the camdisks 49, 50 approximately in horizontal alinement -with the controlshaft 41.

Fig. 2A shows the normal positions of the parts disclosed in Fig. 2, andfrom Fig. 2A, it will be noted that, prior to the operation of themachine, the relation of the median courses of the two complementary camgrooves 49 and 50 to the ends 52 and 53 of the stud at the upper end ofthe intervening crank lever arm 54 is such that the cam disks 49, 50 maybe slid in either direction to t oneor the other of the cam grooves 49',50' over the adjacent protruding end 52 or 53 of the stud at thel upperend ofsaid intervening crank arm 54. In their normal positions, themedian sections between the high or low points of the complementary camgrooves lie in exact alignment or register. y

These complementary cams 49 and 50 enable the operator to select whichcam shall control the movement of the work throughout both oscillationsthereof in opposite directions from the initial position 0f the workWith its toe in contact with the edge rest 31, and the only differencebetween ythe cams is that if the groove 49 of cam disk 49 is tted overthe projecting end 52 of the stud at theupper end of the interveningcrank arm 54, the movement of the shoe will be first to the left, `thenreturning to its initial position, thence to the right followed by areturn to to starting the machine, the operator has rocked the manuallever 5l to the right to fit the groove 49' of the cam disk 49 over theprotruding end 52 of the stud at the upper end of the crank arm 54.

A pair of angularly related divergent arms 54h, 54o, extend downwardlyfrom the hub of the crank lever 54, 54a.

VThe upper ends of links 51, 58 are pivoted to the respective free endsof the angular arms said links being slotted at their lower ends tomutually embrace a stud 59 located intermediate'the ends of, andprojecting laterally from, a floating clutch control lever 60, 60a.

Under emergency conditions the stud 59 forms a pivot for the floatingclutch control lever 60, 60a., as will be explained, but in the usualoperations of the machine, the oating lever rocks on the pivotalconnection 6| at its left hand end with the forwardly extending arm 62of a manually operable emergency lever 62a, 62 pivoted at 63 on the headframe I3.

The emergency lever arm 62 and the floating lever 60, Bform, in eiect atoggle lever which,

at certain times during the operation ofthe inathe slide way and aretail or the pawi earner lever 66, 66a, which serves the same purpose asthe hand emergency lever 62a.

The free end 60a of the floating lever 6I) extends beneath a tappet 61fast on a clutch control rod 68 extending upwardly to control a clutch34 on the countershaft 33, for connecting the main drive pulley39 withthe driving Counter-shaft 33 to rotate said countershaft. y

A spring 68a, one end of which abuts against a guide lug 68D- on thehead viranie I3, through which lug the clutch control rod 68 passes, andthe other end of which spring presses against a collar 68e on the clutchrod 68, holds the clutch normally disconnected.

It will be noted that in the normal idle position of the machine, thecrank arms 54, 54a have been brought by Whichever cam 49 o-r 50 Was lastengaged therewith, into a substantially vertical position coincidingwith the line M (Fig. 2) passing through the pivotal center 55 of' thecrank lever 54, 54', which has resulted in positioning the divergentarms 54h, 54C with their outer ends in the same horizontal plane.

The cam 49 or 50, by bringing the crank lever 54, 54a to its verticalposition and the divergent arms 54h, 54e to their intermediate position,Operated to relax the support afforded the floating lever 60, BDa'by theconnection of the bridle links 51, 58 with the floating lever stud 59,Whereupon the clutch disabling spring 68a forced the clutch control rod68 downwardly to disengage e the clutch members 34 and disconnect theconstant drivepulley 39'and counter-shaft33.

Oscillating shaft drive and in addition, has fixed thereto a face cam 66(Figs. lnand 2) having a cam grooveI 69' formed on one side face, whichgroove is engaged by a roll mounted on one arm of a bell crank lever- 10pivoted at 10' on the head frame |3.

A link 1| pivotally connects theremainingarm of the bell crank lever 10with a slide block 85 (Figs. 2a, 5 and 6) fitting and shiftable andupand down in a slide Way 86' pivoted near its upper end at 81 to thehead irame"|3 Y The link 1I is pivotally connected at 84 to the slideblock, and a connecting link83`securedat" one end to the same pivot 84,extendsto and' is pivotally connected at 82 with the tail of theA pawlcarrier 13journaled on the extension of one of the bearing sleeves 18 inwhich the oscillator shaft 2| is journaled.

Obviously, the angular relationv of the connecting link 83 and the pawlcarrier 13" varieswith the position of the slide way 86 in vrelation.

to the vertical indicated bythe dash line M. 'on Fig. 2. l

To enable the slideway to be rocked first to one side of the verticaland then to the opposite' side thereof, a radius link 56 pivotallyconnects the lower arm 54a ofv the cam-controlled crank lever 54, 54a,with the slide way 86 atk 91.

In the normal positions of the parts as shown in Fig. 2A, the cranklever arms 54, 54a bei-ng: in their vertical positions, wherein: theyhave enabled the spring-pressed clutch control rod 68 to disengage theclutch 34 between the normally idle countereshaft 33 andthe power pulley39`,'it,-will be noted that the radius bar' 56 normally holds theoscillating slide way 86 in its vertical posi-jv tion and that the slideWay, in turn, through the connecting link. 83 between' the slide block:85 ink 13, holdsthe pawl carrier 13 in verticalposition to which it hasbeen returned by the pinions sequence of operations.

Spring-pressed centering arms 19 (Figs. 5 and 6), independentlyjournaled at theirinner ends on the bearing 18 of the oscillatory shaft2| adjacent the pawl. carrier assist in such return, the outer ends of'athe centering arms terminating in radially projecting' `aws 19'," which,when the pawl'carrier isin its normal vertical position, embrace a fixedstud 11 (see also Fig. 5a) projecting from the head frame I3, and also astud 16 projecting laterally from the inner face of the double actingpawl 15.

In this position of the double-acting pawl,

The idle position of the machine, the clutch lever |32 (Figs. 1 and 3)maintains the clutch membersf43, 44 disengaged and the studv |24-(hereinafter referred to) Figs. 1 and 3, projecting from the large gear46 will occupy substane tialIy the position shown. in Fig. l about 180degrees distant from the shift lever |23 to operate the latter near theend of the second "l advance of the control shaft 41. f

Work retaining means At' the very beginningk of the first quarterrevolution the peripheral cam groove 48' (Fig. l) of the cam disk 48fast near the inner end of the control shaft 41, acts on a roll |34"projecting from an oiset finger onthe upper free end of a retaininglever |34 into the cam groove.

The Work retaining lever is of suitable thick-v ness and is pivotallysecured at |33 to the head frame I3 at a point beneath the cam disk 48,the upper end of the retaining lever" being grooved transversely of itsupper wider end at |43, which groove is laterally recessed, as at |42 toform a'pocket having alower wall formed on `divergent angles'.' Frictionlocking rollsv |31 are located within the pocket, onel on each side ofthe central high point towards' which the rolls are respectivelyspring-pressed', to normally engage and frictionally gripf a brake strip|38 seatedy in the groove and extending over the' rolls; whereby thebrake strip |38 is snuglyl held against longitudinal movement betweensaid rolls and the opposite wall of the groove- |43 in the retaininglever |34. y

One end of the brake stripv |38 is pivotally connected to the adjacentend of a pilot and spring terminal2 |381 the opposite end of the pilotand terminal being telescopically entered in the open end of a socket|41'. theV closed end of which is pivotally connected at |44 to the'rocking work support 3. A spring |48 anchored at' the inner' closed endof the socket, isl connected at its outer f centralV point between thefriction gripping rollsV |31Il from which the tooth is normally heldwithdrawnby a spring |45 to free the' rolls for gripping action.

When the work-retaining cam 48 is in its normal idle position, the roll|34a of the retaining lever |34 has been shifted by the cam groove 48 atthe end of its preceding operation, to the left to engage the laterallyextending tail of the trip member |35 with a stationary stud |35 mountedin the head frame I3. Such engagement rocked the trip membercounterclockwise (Fig. 1) to project its wedge-shaped tooth between thefriction locking rolls |31, separating them so as to deprive them oftheir locking action on the brake strip |38 by forcing the rolls towardsthe wider ends of the recess |42.

Release of the friction clutching action of the rolls |31 on the brakestrip |38 enabled the operator to rock the work holder.3 and work awayfrom the edge rest, assisted, it may be, by gravity. A

The spring |40 serves as a flexible link between the work holder and theedge rest to enable yielding movement of the work support relatively tothe edge rest during oscillation of the work to compensate for theirregular contour of the shoes, and for various sizes of shoes whilemaintaining snug contact between the shoe and the edge rest.

It will be recalled that-after rocking the work holder 3 and the shoe inoperative relation to the edge rest, during which rocking the brakestrip |38 slides idly along the groove |43 in the retaining arm, theoperator, having engaged control cam 49, say, with the upwardlyextending arm 54 of the crank lever 54,l 54a, depresses the pedal |28(Fig. 3) to free the gear clutch 43,- 44 for operation.

Thereupon the pinion 45 is given a single complete rotation and drivesthe large gear 46 with its control shaft 41 and the cams 48, 49 and 50through a quarter revolution.

The cam groove 48 of the work-retaining cam 48 operates early in thebeginning of therst quarter revolution to rock the retaining lever |34to the right (in Fig. l), thereby withdrawing the tail of the tripmember |35 from the stud |36. The spring |45 thereupon retracts thewedge-shaped tooth of the `trip member from between the spring-pressedlocking rolls |31 which immediately ride up their respectiveinclines totightly grip the brake strip |38 and hold the latter and the work holderin position with the work in contact with the edge rest 31. The camegroove 48 maintains the retaining lever |34 against rocking movement tothe left until the close of the final quarter revolution of the cam 48,but'l the contour of the work as it is rotated relatively to the edgerest may force the pivoted work support outwardly against the tension ofthe spring |40. i

Meanwhile the control cam 49 (Figs. 1 and 2) associated `with the powercontrol crank lever arm 54 has been gradually shifting the crank lever54, 54a counter-clockwise from its normal vertical position, thedivergent arms 54h, 54o moving with the crank lever in counter-clockwisedirection.

,The depending arm 54a of the crank lever 54, 54a, on saidcounter-clockwise travel, thrusts the radius link 56 to the right torock the slide wayv 86 to the right to the position indicated by theline I Fig. 2.

Because of the approximate concentricity of the pivotal connection 04 ofthe pawl carrier link 83 and slide block B5 with the pivot 81 of theslide way 86, the rightward adjustment of the slide way by the controllever armur54a only slightly shifts the lower end of the link 1| alsoconnected with the slide block at 84, and the pawl carrier 13.

Such slight shifting of the pawl carrier may be sufficient to displacethe pivot 14 (Figs. 5 and 6) necting the power pulley 39 with thecounter shaft 33 is still disengaged, no movement is imparted to thepower transmitting bell crank 10.

However, the divergent power clutch controlling arms 54b,54c, on theircounterclockwise travel with the control crank lever 54, 54a, about thestud 55 as a center, operate, the arm 5419v to lower its slotted link 51relatively to the stud 59 on the floating clutch control lever 60, 60aand the arm 54e to raise its slotted link 58, so

' that the lower wall of the slot in contact with the stud 59 will rockthe floating clutch control leverl counterclockwise on its pivot 6| andpress the free end 60a of such lever against the tappet 61 on the clutchcontrol rod 68.

The slotted link 58, in its continued upward movement causes the clutchcontrol lever arm 60a to lift the clutch control rod 6B against thetension of its restoring spring 68a and as the rst quarter revolution ofthe gear 46 and contiol shaft is completed, the clutch 34 connects thepower drive pulley 39 with the counter-shaft 33 to rotate the power cam69 and the remaining cams (not shown) controlling the actuation of thepunching and tacking mechanisms operating on the shoe.

Just prior to the end of the first quarter of a revolution, the highpoint of the control cam 49, as shown in Fig. 2, has rocked the controllever 54, 54a to the position indicated by the line I corresponding tothe position I of the slide way, where it is held during the followingoperation to maintain the slide wayA 86 in its inclined adjustmentduring the reciprocation down and up 0f theslide block 85.

The operator having removed his foot from the pedal starting lever |28,the springs |28c and |30() (Fig. 3) have restored the pedal lever andthe intermediate lever |30 to their normal positions, the spring l30b inaddition returning the starting clutch control lever |32 to position todisengage the clutch members 43, 44 at the end of one complete rotationof the pinion 45, as the large gear 46 completes ,its advance of aquarter revolution.

Therefore, the control shaft 41 and control cams 49 and 50 ceaserotation together with vthe retaining cam disk 48.

The high point of cam 49 acting upon the control crank lever 54, 54a,maintains the slide way 86 at the extreme right hand limit of travel1First quarter rotation .It Will be recalled that the active control cam49 or 50 (Fig. 2) on the first quarter rotation of control shaft 41,operated the floating clutch control lever 60, 60a, to connect the powerdrive pulley 39 with the counter shaft 33 through the clutch 34, thisconnection being timed to occur substantially as the active cam iscompleting its rst quarter revolution, and as its power connection isdisengaged.

Thereupon, the drive pulley 39 starts rotation of the counter shaft 33and the drive cam 69 (Fig. 2) together with the cams (not shown)controlling the punching and tacking mechanisms. Because of the four toone ratio between the large gear 46 and the pinion 45, the pulley 4I ofwhich is about the size of the drive pulley 40 fast with maindrivepulley 39, it is obviousfthat the shaft 33, when driven by the pulley'39, will make a complete rotation in approximately the same time thatthe controll shaft 41 makes. av quarter -of a revolution.

' Normally, the roll on the shorter arm of the bell crank (Fig. 2) liesat the loW point ofthe drive cam 59, as shown in Fig. 2a, and the slideblock 85 lies at the upper end of the slide way 86 adjacent to orpartially over-lapping the pivotal center 81 of the slide way (Fig. 5).,Also the pawl carrier 13 is in its substantially vertical position. Dueto the previous shift of the slide way to its inclined position duringthe rst quarter. revolution of the controlshaft 41, a slight movementmay be imparted to the pawl carrier through its link connection with theslide block 85, sufcient to engage the proper tooth ofthe double actingpawl 15 with the friction disk 12.

Therefore, the drive cam 69 as it makes a come plete rotation, imparts aquick oscillation to the bell crank 10 which movementis transmittedthrough the connecting rod 1 I, slide block 85 and link 83 to the pawlcarrier 13. The block 85 sliding smoothly down theinclined slide way 8B,first draws the link 83 to the right (Fig. 6), to impart a clockwiserotation to the, pawl carrier 13, and on its return, forces the pawlcarrier back to a substantially vertical position.

If the pawl is not already in frictional engagement with the frictiondisk 12 at the outset of the clockwise advance of the pawl carrier, thestud 16 of the do-uble acting friction pawl 15will contact with the jaw19 ofthe left hand centering arm 19 which causes the pawl to rock untilits left hand tooth grips the friction disk 12 to impart apartial'rotation to the `friction disk and the oscillatory shaft 2 I,which movement is transy mitted through the bevel gears 5 (Fig. l) tothe block 85 as it is forced downwardly inthe slide way 86, and hencepressure is communicated to the slide way tending to restore it toa'vertical position, but such pressure is opposed by the radius link 5Bbetween the slide way 86 andthe crank lever 54, 54a. i Rotation of theoscillatory shaft 2|, which rotates the work support,' is alsotransmitted through the gear |05 (Fig. 1) fast on the opposite end ofthe oscillatory shaft, to the gear |06 fast on the corresponding. end ofthe return shaft |01 journaled inthe head frame parallel with andbeneath the oscillatory shaft.

The return shaft |01-supports a pair of opposed collars |08ffast on theshaft. Oppositely coiled springs |I0, II| on the respective collars areheld in tension by contact of the outer end of each spring with atraveling pin |09 project ing laterally from a radial arm on each of`said collars |08, the opposite endv Illia, IIIa of each spring |I0,`|II contacting the respectively op posite sides of an anchory pin' II3supported intermediate its ends on a post |I2 projectingupwardly betweenthe two opposed springs I I0, I I I.

Rotation of the oscillatory shaft v2| inv either directionby the pawlcarrier 13, pawl 15 and friction .disk 12 will'operate through the gears|05, |06 to rotatel the return shaft |01 and further tension one or ltheother of the already tensioned return springs |I0, III by movement ofits traveling pin |00 in a direction to wind the corresponding springmore tightly; Obviously, one spring or the other will be coiled moretightly depending upon the direction in which the return shaftl |01 isrotated by the pawl carrier 13 and pawl 15, that spring not being woundbeing slightly relaxed or uncoiled due to movement of its traveling pin|09 towards the anchoredy end of the spring.

As the driving cam 69 (Figs. 1 and 2) through the bell crank 10 and link1| retracts vthe slide block 85 upwardly along the inclined slide Waywork holder or support 3 to shift the toe portion of the shoe to theright While still pressed against the edge rest 31, so as to feed theshoe relatively to the working tools for a limited distance along l theleft hand side of the toe (Fig. 9a), during the operation of thepunching and tacking mech-l anisms, simultaneously operated by thecounter shaft 33.

The stud 1B of the pawl 15, as the pawl carrier proceeds on its advancestroke, forces the left hand centering arm 19 leftward (Fig. 6)tensioning the spring 80 connectingthe two centering armsthe right handcentering arm being held in normal .position by contact of its jaw 19',with the stationary stud 11. y

Obviously, .the resistance opposed to the advanceoscillation of the shoeorworkand inertia of ltheparts is overcome by the power/driven ,slidecarrier.

86, the pawl carrier 13 is rocked counter-clockwise back to its normalvertical position, at the beginning of which movement the left handtooth of the double-acting pawl 15 disengages from the friction disk 12.L. l

Such return movement of the vpawl carrier is assisted by the centeringarm 19`unde1 the ten# sion of the spring 80, which acts to insure anaccurate-centering of the pawl carrierand its pawl in their normalverticall positions.

Upon release of thegripping action of the pawl 15 on the friction disk12, the oscillatory shaft 2| controlling the rotation of the worksupport would ordinarily be free to be returned with the work to itsnormal position Aunder the stored tension of the spring II0 or III, atthe Very beginning of the return movement Aof However, the main driveshaft 33 is still operating to restore thev slide block 86 andfthe pawlcarrier to'their .starting positions, andthe return-of the work beforethe tools Vhave ceased to operate should be prevented.

Tothis end, that side of the friction disk 12 facing the. adjacent sidewall of the head frame I3, is circularly chambered (see Fig. 7a) to ace.commodate a circular brake .member 90 (Figs. '7-8) j ournaled on theprojecting shouldered end of the bushing 18 fast in'the head frameandextending into the chambered portion of the friction disk 12.

l Opposed arcuate grooves formed near thejpe-r riphery of the circularbrake memberl90' extend from the respective opposite ends ofajperipherally formed recess |49 inthe brake member.

Springs 96 seated in the respective opposed arcuate grooves pressagainst the adjacent ends of arcuate followers 95 to maintain theopposed ends of such followers in contact with friction rolls 92, 93located on respectively opposite sides of a stationary separator 94projecting from the head frame |3 centrally -into the peripheral recess|49, opposite a pair of divergently inclined braking faces' 92a, 93a,locatedcentrally, and forming a part of the inner wall, of the'recess|49, the rolls 92, 93 adapted to bind between lone or the other brakingface and the periphery of the chamber in the friction disk 12, dependingupon the direction in which the brake member 99 is rocked, to lock thefriction disk, its oscillating shaft 2|, 'the work holder 3 andthe workagainst return at this time to their normal starting positions.

A link 89 pivoted at 90 to the braking member 90, connects the memberwith the adjustable slide way 86 at 88.

In the normal vertical position of the slide way 86 (Fig. '1), the linkconnection with the brake member 90 maintains the braking faces 92a, 93acentered beneath the separator 94 and the spring-pressed followers 95maintain their respective rolls 92, 93 against the respective oppositeedges of the separator 94, the rolls resting on the lower ends of thebraking faces 92a, 93a, so that no braking action can occur, and thefriction disk 12 can freely rotate in either direction.

During the first quarter rotation of the active control cam 49 or 50which rocks the control crank lever 54, 54a, to swing the slide way 86to one side or the other from the vertical position, the slide way,through its link connection 89,

rocks the brake member 90 to the position shown i in Fig. 8, or to theexact reverse of such position, depending upon which control cam iseffectively connected with the slide way.

Rotation of the brake member 90 clockwise,

as in Fig. 8, for instance, shifts the divergent braking faces 92a, 93a,awayfrom the left hand roll 92 which is held against movement in thesame direction by the separator 94, and its spring 96 is merelycompressed. Therefore, the left hand roll 92 resting in the deeper orWider portion of the recess, can exercise no braking function.

But as the brake member 90 rocked clockwise, it shifted its right handinclined braking face 93a farther beneath the co-acting friction roll93, and the tendency of the roll to accompany the brake member 90 beingretarded or resisted by its associated spring-pressed follower 95, thefriction roll 93 is brought to a position where it can bind between thebraking face 93a and the inner periphery of the friction disk 12 as soonas a reverse motion of the friction disk is attempted.

The rotation of the friction disk 12 by the pawl `carrier 13 and pawl 15to turn the work rotating shaft 2| in a direction to advancethe workfrom its normal starting position, turns the friction disk in the samedirection in which the braking member 90 was turned so that no bindingaction of the friction rolls 92, 93 can occur at this time.

But when, upon the release of the friction disk 12 by the double-actingpawl 15 at the very beginning of the return of the pawl carrier 13towards its starting position, tensioned return spring or starts torotate its return shaft |01 and, through gears |09,l |05, theoscillatory shaft 2| and friction disk 12 in the opposite direction, thefriction roll 93 (in the present instance) Fig. 8, will immediately gripthe frictiondisk 12 locking it, together with the oscillatory shaft 2|and the work against restoration to their starting positions.

This locking action is rendered possible because the high point of thecontrol cam 49 (say) Fig. 2, is still maintaining the slide way 86 andhence the braking member 9|) stationary in their rightward adjustedpositions.

This restraining action of the friction' rolls 92 or 93 binding betweenthe friction disk 12 and braking member 90 will be maintained until theend of the second quarter rotation of the control shaft 41.

Second quarter rotation Clutch tripping studs ||4, ||5 (Figs. l and 3)adjustably mounted in spaced relation on the outer face of the gear |06project laterally into the vertical plane of the upright arm ||8a of amultiple-armed lever |18 journaled on an axleA ||1 projecting from thehead frame |3 in vertical alinement with and beneath the work-returnshaft |01.

Divergent arms H81), ||8c depend at substantial right angles to eachother from the hub of the multiple-armed lever ||8 of which theyconstitute a part. Links |25, |26 individual to the respective dependingarms |1811, |8c are pivoted to the outer ends of said arms, therespective links being slotted at their lower ends to embrace theopposite ends of a pin |21 passing through the rear arm of the pedallever |28. The lpedal restoring spring |28c acting through the pedallever |28 and pin |21 normally centers the multiple armed lever ||8.

Consideration of Figs. l and 3 will indicate thata rocking of theupwardly extending arm ||8a in either direction is effective to rock thedepending arms HBD, ||8c to thrust one slotted link downwardly and pullthe remaining link upwardly, thereby rocking the pedal lever |28clockwise to cause the clutch control lever |32 to release the clutchmembers 43, 44 for operation, resulting in another complete rotation ofthe pinion d5 and another quarter of a rotation of the control shaft 41.

It will be recalled that immediately subsequent to the completion of thefirst quarter rotation of the control shaft 41 and as a result thereof,the clutch 34 connected the counter shaft 33 with the main power pulley39 which imparted a partial rotation to the work oscillating shaft 2|,and that said work oscillating shaft, in turn rotated the l restoringshaft |01 through the gears |05, |06, after which, continued rotation ofthe cam 69 in making one complete revolution returned the slide blockand pawl carrier 13 to their normal positions.

The pawl carrier 13 at the end of its advance stroke has imparted arotation of such extent to the oscillatory shaft 2| and the gears |05,|06 as to cause the stud H4 on the gear |06 to collide with and rock thearm |8a of the multiple armed lever ||8 in clockwise direction. Themultiplearmed lever through link |25 rocks the pedal lever |23clockwise, tripping the control shaft clutch 43, 44 for operation.

Therefore, as the drive cam 69 is completing 'its single cycle ofrotation, and restoring the slide block 85 and pawl carrier 13 to theiridle positions, which occurs with great rapidity, the pinion 45 isstarting the rotation of the large gear 4B to impart thesecond,quar-terrevolution to the control shaft 41.

The cam groove 48 of the v vork-restrainingk cam 48 continues to holdthe work against the edge rest throughout such second quarter rotation,but the groove 4;!3` of the control cam 49, shifts the control cranklever 54, 54a to the vertical or median position indicated in Fig. 2 bythe i line M and 'through the radius llink 56,A swings the slide way 86back to its vertical median posi tion also indicated by theline M inFig. 2.

The slide way, in turn,through link 489 (Fig. .8) returns the brakingdrum 90 counterclockwise (in Fig. 8) to its normal position, and asksoon as the lower surface of the inclined braking face 93a has released.the friction roll 93, the #tensioned return spring reversely rotatesthe return shaft v|l1 and through gears |06, |05 restores theoscillatory shaft 2|, the work support and the .work

to normal starting position.

' The projecting stud I|.4 (Fig. 3) on 'the gear wheel |06 has been.holding the multiple-armed lever IIB in its counter-clockwise position,and' hence the pedal lever |28 is held in actuated position,notwithstanding the return of the intermediateclutch lever |30 andclutch .control lever |32 to their normal positions. But upon thereverse rotation of the restoring shaft |01 by the tensioned spring I|0,the gear stud I4 releases the multiple armed lever v||8 and pedal lever|28 At the end of this second quarter rotation the shoe I is again incontact with the edge ple-armed lever ||8 in a direction transverse toits pivotal motioni The lever arm ||9 projects lupwardly behind '.(tothe left in Fig. 1) the gear .wheel |06 fast on the return shaft |01,where it is shiftable into `and out of the path of a stud I|.6\proJ`ecting from the rear face ofthe gear |06.

Aspring 1| 2.0.normally holds the upperfree'end of the lever arm IIS outof the path of the stud ||6 and in contact with the broadened dependingarm of vthe .bell crank lever |2I.

' The mamme-armed lever Ila, it will be re-" called, is connected withthe starting pedal lever |28 in, such manner `that rotation ofthemultiplearmed lever .H3 .in either direction will operate the pedallever '|28 to release the control shaft clutchmembers 43, 44 foi,ac'tioi1.y It Awill vbe recalled also that the first quarter rotationof the control shaft 41 resulted in tripping the vcountershaft drivingclutch 34, to impart the rst advance of the oscillatory Work traversingshaft 2| which, inturn, resulted in Vautomatically 'tripping the clutch43, 44 to ven- Vable a second quarterrotation of the control shaft 41which, in turn, resulted in disconnecting the counter-.Shaft clutch 34.Meanwhile during apart of the second quarter rotation of the'control vsljlaft .41, the oscillatory work traversing shaft rest 31, the-clutches34 and 43, 44 are' disengaged and the slide way 86 andthe pawl carrier13 4are in their vertical positions. Clutch 43, 44 was disengagedbecauseof the presence of the,

clutch control lever |32 in the path of the clutch as the lattercompletes its single revolution.

Third quarter rotation I The large gear 46. (Figsrl and 3) which i'sadvanced always in one direction by quarter revolutions, carries on itsinner face a projecting stud |24 which, in the normalhome position ofthe gear, lies vertically above the shaft 41` of the gear. At the endrofthe rst quarter revolution of the shaft 41 and gear 46, the stud ,hasadvanced to the position shown in Fig.' 3,-where it projects above butisstill nearly7 one step apart 'l from a lever |23 pivoted at |46 to thehead frame I3. This lever |23 'is connected by a rod |22 with theVrearwardly extending arm of a bell crank'lever |2I pivoted at |41 to thehead frame.`

The depending arm` of the bell crank |2| is Widened to afford a surfaceof suilcient area for engagement by thefree end of a forked lever ||9transversely embracing the hub of the multiple-armed starting clutchtripping lever ||8 to which it is pivoted at |48. AIt will be noted thatthe lever'arm 9 is rockablegon itspivot v|48in one direction and alsocan turn with the multi-.

of the control shaft 41, the tip of the toe of 45.

onthe Vgear, |06 has advanced from .shown in Fig.. l. to .that shown inFig. 3.

2| and its connected gears |65,l |06 remained in the positions to whichthey wereadvanced, due

tothe restraining action of the brake'mechanism 0.10, 9 3 on thefriction disk 12.

Then, Vneartlie vend of the second quarter rota- .tionof thecontrolshaft 41, thev brake vis released to'enable `the tensioned springIl 0 to restore theoscillatory work traversing Shaft .2| and work holder3 .to their starting positions, by reversely rotating the gears |06,v I05.

fWhen the machine is at rest in its normal position, the ,projectingstud 'I I6 on the inner `faceof the gear |06 lies opposite the free endof .the pivotedlever `arrn |.I9 .which', at that time,

is held by its spring I20` in contact with thefbroadeneddepending armofthe idlebell crank 2 and outfof thepathororbitof the'stud |6,as'sliown. Ain-Eig. 1.

However, `asa result of .advancing the oscil- -latory .work traversingshaft 2| and thegears |05, ,|06`,. on the r'stadvance stroke of thepavvl carrier .1 3,.immediately,followingthe rst quar-y ter .rotation oflthe control shaft 41, the stud .I I6 its position This .advance, asheretofore explained,occurs prior .to .thefsecond .quarter or .rotationofthe `,controlshaft4,1, and .thebrakemechanism 90, v|l3-retains thegear |06 and its stud .I |16- inl such advanced `position-duringa partof the ensuing secondduarter 4rotation of the control shaft 41. vl'-riorto thecompleterelease of the brake mech- -vanism 80, 93 .and the.operation of the tensioned `spring motor |I0to restore the oscillatoryshaft 2 I ,which occurs lat .the end. off such second. quar-.ter-rotation` ofthe control shaft41, thestud |24 onthe large gear 46ywhich advanced: to-ft'heposition shown in Figr 3 on theprecedingfrstlquare .ter rotation of said,shaftfadvanceswith thelargegear 46 during such. second ,quarterloperatmn to shift the leverarmllfinto V,the'return path Tlie,control.,shaft.4f1 with-itslgeard comes torestatf the endof thelsecondduarter rotation of the con-trolshaft (-due.to the completion ofi rotaing and punching mechanisms,

rocks the pedal lever clockwise and trips the control shaft drive clutch43, 44 for operation in the same manner as heretofore explained, thestud l I6, as it returns to its normal position, holding themultiple-armed lever ||8` in its rocked position, although the pedallever |28 as usual, after tripping the clutch 43, 44, escapes past theintermediatelever |30, which immediately restores to *normal with theclutch'trippinglever |32.

The pinion 45 makes its third complete revolution upon the tripping oftheclutch 43, 44 to advance the control shaft 41 through its thirdquarter of a revolution.

One of the first results is that the stud |24 which initiated the clutchtripping operation, escapes past the lever |23, which'together with the.pedal lever |28 return tonormal under the influence of pedal leverspring |28c, thus freeing the lever arm ||9 for return to its normalidle position by the spring |20.

The control cam 49 turns a quarter revolution to present its low pointto the roll 52 at the upper end of the crank lever 54, 54a which resultsin swinging the crank lever from the vertical Y position last occupiedto the inclined position indicated by the line II (Fig. 2) and similarlyswinging the slide way 86 from its vertical posi- ,tion to the positionindicated by the line II adjacent the slide way in Fig. 2.

These inclined positions of the crank lever and slide Way are just ,thereverse of those occupied by these elements as a result of the firstquarter rotation of the control shaft 41.

The crank lever 54, 54a, as it is rocked clockwise by the control cam49, rocks the divergent levers 54h, 54o, in like direction, to cause thelink 51 to swing the floating clutch control lever 60, 50acounter-clockwise, lifting the clutch rod 68 to render clutch 34effective as the third quarter rotation of the control shaft 41 iscompleted.

The vdrive cam 69 upon its connection with the power pulley 39 throughclutch 34 and countershaft 33, actuates the bell crank 10 and link I1|to impart a rapid -reciprocation down and back to the slide block 85traversing the slide way, and through link 83, rocks the pawl carrier 13and its pawl 15 counter-clockwise and then back to their normal verticalor substantially vertical positions.

Because this movement of the pawl carrier due to the reversed positionof the slide -way 86 is just the opposite of the movement of the pawlcarrier during the iirst quarter rotation, the friction disk 12 impartsa movement to the oscillatory shaft 2| and the Work support 3 in adirection to present the right side of the toe of the shoe to the tack-Also the oscillatory shaft through gears and Hl'a` transmits a reverserotation to the return 'shaft |01 to tension motor spring Adjustment ofthe slide way 86 clockwise to its II position during the third quarterrotation of the control shaft 41, conditioned the restraining brakemechanism 90, 92 for operation, the brake 'member 90 having been rockedlcounter-clockwise through its rod connection 89 with the slide way sothat the formerly effective friction roll 93 is rendered ineffective andthe opposite friction roll 92 rendered effective.

Therefore, the' motor spring is prevented from restoring the worksupport and work to their initial positions at this time.

Fourth, quarter rotation At the end of the third quarter rotation of thecontrol shaft 41., the stud |24 (Figs. 1 and 3) on the inner face of thelarge gear 46 was brought to its nine oclock position and near the endof the subsequent advance throw of the pawl carrier 13, incounter-clockwise direction, a stud l5 adjustable on and projecting fromthe outer face of the gear |06 fast on the return shaft |01,.col lideswith the arm ||8a of the multiple-armed lever H8 to operate the pedallever |28 and release the control shaft clutch 43, 44 for operation.

Thereupon, and while the oscillatory shaft 2|, its work support 3 andthe work is still maintained by the braking mechanism in their advancedpositions, the control shaft clutch 43, 44 starts to drive the controlshaft 41 through the final or fourth quarter. of a complete revolution.

As a result, the control cam 49, the low point of which has been holdingthe crank lever 54, 54a and the slide way 8G in their clockwisepositions' as indicated by the lines II in Fig. 2, starts to returnthese elements to their vertical positions M, the angular arms 54h, 54e,turning counterclockwise with the crank lever, to enable the slottedlink 51 at this time maintaining the floating clutch control lever 60,60a in its effective position, to descend.

Thereupon, the spring 68a, of the clutch control rod |58 forces the roddownward together with the oating lever 00, 60a, to disable thecounter-shaft driving clutch 34 and discontinue the operation of thepower cam 69, slide block 85, pawl carrier 13, friction disk 12 andoscillatory shaft 2| with its connections.

As the control shaft clutch 43, 44 is timed to start to operate prior tothe disengagement of the countershaft clutch 34, the drive cam 69 isenabled to complete its revolution, the slide block 85 is brought up toits normal position, and the pawl carrier 13 returned to a substantiallyvertical position as the countershaft clutch comes to rest. I

Following these operations, the continued movement of^the crank lever54, 54a and slide way 86 clockwise towards the vertical turns the brakedrum 90 clockwise a suicient distance to relieve the braking action ofthe roll 02 on the friction disk '52,' ywhereupon the tensioned spring|l| restores the return shaft |01 and through gears |00, |05, restoresthe oscillatory shaft 2|, the work holder 3 and the work to theirinitial startingpositions. At this time the appropriate spring-pressedcentering arm 19 acts to correctly yposition the pawl carrier 13 andpaWl 15.

At about the same time, the work support restraining cam 48 (Fig. l)will shift the restraining lever |34 counter-clockwise, relaxing thetenrest 31, to remove the nished work andsubywork to present the righthand side of the rtoe of the shoe to the tools, rotated the gear |06with its studs I I4, II and H 6 in counter-clockwise direction whentensioning the motor spring I I I.

This movement of the gear |06 was without consequence so far as thetripping studs I I4, II5

were concerned, but the stud I I6 was brought to the left of thepivote-d clutch-tripping lever arm II9 (Fi-gs. 1 and 3).` However, thecondi'- -tioning stud |24 which was left `in a position to the left ofthe control shaft 41 at the end vof the third quarter rotation of saidshaft, is brought Ito its normal `position vertically above the shaft 41at the end of the fourth quarter rotation and hence does not operate thelever 423 to vshift the pivoted lever arm I I9 into the returnA path ofthe tripping stud IE6. f

'Consequently,as the motor spring YI I I returns the gear IDB to itsnormal' position, the stud I I6 merely returns to its normal positiondirectly in front of the pivoted lever arm without colliding therewith.

Hence, as neither of the'clutches 34 01143, 144 is tripped, the machinecomes to rest. 1

From the foregoing description,'it is yclear that the work isintermittently'presented to the tools at regular intervals and "forregular'periods of time.v i f During the operation of the machine, ifany reason should develop justifying an immediate stoppage of operation,as failureLof the toolsv through breakage or lack of material, theoperator may manually rock theV emergency lever 62a (Fig. 2) or depressthe treadle 66a, either of which will ileX the levers 62, Ell, ayattheirpivotal connection 6I in the manner of, a toggle lever to immediatelyfree the clutch control rod 68 to the action of its spring 68a, which atonce disengages the counter vshaft driving 'clutch 34,

Idepriving the drive cam '69 of power to yactuate' the pawl carrier 13,and the machine Comes to rest, with its parts in their partially,operated positions. l

In' this operation, they floating lever (il), ,60a pivots on the stud 59as a fulcrum, as shownin dotted lines in Fig. 2.-

' After repairing the fault, return of the manual lever l62a. to itsnormal position willre-engage the clutch'34 and the machine willcomplete the interrupted operation.

support '3 and'work by the oscillating. shaft; 2l

may be varied or adjusted to a limited extentacrcording to the size ofthe shoe loperated upon; or

to the stretch of shoe desired tobe tacked. v

To this end the pivotal connection 91 `(Fig, 2)

, of the radius link 56 tothe swinging slide way 86 may be arranged for`adjustment lengthwise of the rear face ofthe sliderway, by meansof anadjusting lever IUII pivoted at IDI, a suspension link 98 beingpivotally connected at S9 -to the free end of the adjusting leverandsupporting the pivotal connection 91 at its lower vend. By swingingthe adjusting Alever I in oney direction or .the other, from theposition shown in Fig. 2, to one or another of the recesses I'5Il whilethe machine .is at lrest with the slide way in its vertical position',the connection `91 is moved relatively to the pivotal support 81 of theslide way to enable the radius rod under control of the cam 49 or 50, toposition the slide Way 86 to one side or the other of the vertical at agreater or lesser angle, it being remembered that the cam groovecontours 49', lEll are'xed'and i always impart the same` degree ofAthrow to the l slide Way. f The adjustment of the extent of inclinationwhich may be assumed by the slide way 805v also results in varying thedistances or spaces between the fasteningsapplied vto the shoe, asindicated inFigsQa to 9c. O

What is claimed is:

1. vIn a shoe tacking machine, the combina'- tion with a work support;an edge rest against which the work is held; and a constant power drive;of an oscillatory'shaft connected with the work support; a countershaft;a normally disconnected clutch between the power drive and vthecountershaft; means operable by the counnormal intermediate positionsubsequent to each advance of the oscillatory shaft.

2. A shoe tacking machine, including a work support for the Work; anedge rest against which the work is pressed; a power drive; anoscillatory shaft connected With'the work support'to rotate the latter;normally idle means operable by 'the power drive to positively rook thework support and work first in one direction and later along one side ofthe toe of the shoe can be performed intermittently instead of by acontinuous succession of operations, if desired.

Or by holding the emergency lever effective and manipulating thevpedallever I23,the shoe may be returned to itsy initial starting positionVand the work holder 3 released to permit rea partial operation ofl `atany other time vthan when the countershaft 33 is beingpower driven. I

The vcam 69 operates the means for properly presenting the work to thetools, and the cams 449, 5D condition such `means for operation in onedirection 'or the other. i

rllhe extent'o'f oscillationlimparted to 4thework in the oppositedirection from a normal inter` mediate or starting position; means todetain the work support and work in either of itsv advanced positions;means to release said detaining means;

and means to restore the work support and work k to its normalintermediate or starting position after each said advance, upon therelease ofsaid detaining means. i y y 3. A shoe tacking machine,including a rotatable work support; an edge rest against which the workon the work support is'pressed during rotation of the supporta powerdrive; normally idle means operable by the power drive to positivelyrotate the work support and work, first, in one direction and llater inthe opposite direction from a normal intermediate or starting positionin each instance; a" normally disconnected clutch between the powerdrive and -the work-support rotating means; means advancing through acomplete revolution by successive steps, to control the alternateconnection and disconnection of the clutch according to the step towhich the means has been advanced; an automatically disengaged couplingbetween the power drive and said clutch control means; means controlledby said work support rotating means to render the coupling effective;and means to restore the work support and work to their normalintermediate or starting positions subsequent to each advance of thesupport.

4. A shoe tacking machine, including a rotat able work support; an edgerest against which the work on the work support is pressed duringrotation of the support; a power drive; normally idle means operable bythe power drive to positively rotate the work support and work, iirst,in one direction and later in the opposite direction from a normalintermediate or startingposition in each instance; a normallydisconnected clutch between the power drive and the worksupport rotatingmeans; means advancing through a complete revolution by successivesteps, to control the alternate connection and disconnection of theclutch according to the step to which the means has been advanced; anautomatically disengaged coupling between the power drive and saidclutch control means-means controlled by said work support rotatingmeans to render the coupling effective; and opposed motor springmechanism operable by said work support rocking means when advancing thework support, to restore the work support and work to their normalintermediate or starting positions subsequent to each advance of thesupport.

5. A shoe tacking machine including a rotatable work support; an edgerest against which the work on the work support is pressed duringrotation of the support; a power drive; normally idle means operable bythe power drive to positively rock the work support and work, rst, inone direction and later in the opposite direction from a normal idleintermediate or starting position in each instance; a normallydisconnected clutch between the power drive and the work support rockingmeans; means rotated by successive steps to complete a revolution tocontrol the alternate connection and disconnection of the power driveandy the work support rocking means; a drive pinion; an automaticallydisengageable one-revolutioncoupling between the power drive and thedrive pinion; a driven gear connected with the intermittently rotatedcontrol means, the gear having a ratio lto the pinion equalvto thenumber of steps required to complete a revolution of the control means;means controlled by said work-support rocking means to render the onerevolution coupling effective; and means to restore the work support andwork to their normal intermediate or starting position's subsequent toeach advance of the support,

6. A shoe tacking machine, including a rotatable work support; an edgerest against which the work on the work support is pressed duringrotation of the support; a power drive; normally idle means operable bythe power drive to positively rotate the work support and work, firstlin one direction and later in the opposite direction from a normalintermediate or starting position in each instance; a normallydisconnected clutch between the power drive and the worksupport rotatingmeans; means advancing through a complete revolution by successivesteps, to control the alternate connection and disconnection of theclutch according to the step to which the means has been advanced; anautomatically disengaged coupling between the power drive and saidclutch control means; a tripping member rockable with said work supportby said power drive; coupling tripping means connected with saidcoupling; means on the tripping member operable upon the couplingtripping means in either direction of travel of the work-support; andmeans to restore the work-support and work to their normal intermediateor starting positions subsequent to each advance of the support.

7. A shoe tacking machine, including a rotatable work support; an edgerest against which the Work on the work support is pressed duringrotation of the support; a power drive; normally idle means operable bythe power drive to positively rotate the work support and work, rst; ineone direction and later in the opposite direction from a normalintermediate or starting position in each instance; a normallydisconnected clutch between the `power drive andthe worksupport rotatingmeans; means advancing through a complete revolution by successivesteps, to control the alternate connection and disconnection of theclutch according to the step to which the means has been advanced; anautomatically disengaged coupling between the power drive and saidclutch control means; means to automatically connect theV coupling,including a clutch closing lever; a double acting trip lever linked tothe clutch closing lever to operate the latter upon movement of the triplever in either direction; means operable with said work support in bothdirections of rotation of the latter to actuate the double acting leverand render the coupling operative; and means to restore the work supportand work to their normal intermediate or starting positions subsequentto each advance of the support.

8. A shoe tacking machine, including a rotatable work support; an edgerest against which the work on the work support is pressed duringrotation of the support; a power drive; normally idle means operable bythe power drive to positively rotate the Work support and work, rst, inone direction and later in the opposite direction from a normalintermediate or starting position in each instance; a normallydisconnected clutch between the power drive and the work-supportrotating means; means advancing through a complete revolution bysuccessive steps, to control the alternate connection and disconnectionof the clutch according to the step to which the means has beenadvanced; an automatically disengaged coupling between the power driveand said clutch control means; means to automat-y ically connect thecoupling, including a clutch control lever; a double-acting trip leverlinked to the clutch control lever to operate the latter upon movementof the trip lever in either direction; means operable with said worksupport in both directions of rotation of the latter to actuate thedouble acting trip lever and render the coupling operative; a normallyidle lever arm shiftably connected with the trip lever; means actuatedby the step-advanced means to shift said lever arm into effectiveposition relatively to the actuating means for the double-acting triplever for operation by said trip lever; and means to restore the worksupport and work to their normal intermediate or starting positionssubsequent to each advance of the support, said last-named meansVoperating the actuating means for the double acting trip lever toeiectan operation of. thetrip lever through the shiftable lever arm.

9. A shoe tacking machine, including a rotatby successive steps incompleting a revolution, to

control the alternate connection and disconnection of the clutchaccording to the position to which the means has been advanced,including a pair of complementary cams and a clutch control leveroperable by either cam; means to select the particular cam which shallcontrol thev clutch control lever; means controlled by either cam toreverse the direction of` rotation of the work support; an automaticallydisengaged coupling between the power drive and the complementary cams;means controlled by the work support rotating means to render thecoupling eifective; and means to restore the Work support and work totheir normal intermediate or start.

ing positions subsequent to each advance ofthe support. 1

10. A shoe tacking machine including a rotatable worksupport; an edgerest against which the work on the work `support is pressed duringrotation of the work support; a power drive; means operable by the powerdrive to positively rotate the work support and work, rst, in one jdirection and later in the opposite direction from a normal intermediateor starting position in each instance, including a counter-shaft; a camon the counter-shaft; a normally disconnected clutch between the powerdrive and #counter-shaft; areciprocatory member driven by the cam; meansto intermittently connect the reciprocatory member and the work support;means to adjust the path of travel of the reciprocatory member to oneside or the other of the vertical position to reverse the direction ofrotation of the work support; `means to control the connection anddisconnection oi said clutch; and means to restore the work support andwork to their normal intermediate or starting positionsr subsequent toeach `advance of the support and at such times as the connection betweenthe reciprocatorymember and the work support is intermittedjy 11. A shoetacking machine including a rotatable work support; an edge rest againstwhich the work on the work support 'is pressed during rotation of thesupport; a'power drive; means operable by the powerdrive to positivelyrotate the work support and work, rst, -in one direction and later inthe opposite direction from a normal intermediate or starting positionin each instance, including a reciprocatory member; an adjustable guidemeans for said reciprocating member; means to variously adjust theangular position of the guide member relatively to the verticalposition, including a cam; a lever controlled thereby; a radius linkconnecting the lever with the adjustable guide means; means'to vary thepoint of connection of the link and the guide means;means to' impart astep by step rotation in one direction to the cam to variously rock thelever, including a normally disconnected coupling between the powerdrive and the cam;

means also controlled by said cam to engage and ldisengage the clutch;and `means to restore the work support and work-to their normalintervwork on the support is pressed diring rotation of the support; apower drive; means operableA by the power drive to positivelyl rotatethe work support and work, first, in one direction and later in theopposite direction from. anormal intermediate or starting position ineach instance, including a reciprocatory member; an oscillatory shaftconnected with the work support; a disk fast on said shaft; anormally'vertical rocking pawl carrier rotatable about said s haft,v adoubleacting pawl mounted on the carrier and effective to turn saiddisk, the shaft and the work support in either direction; means totransmit power from the rcciprocatory member to, the pawl carrier; meansto rcontrol the path of reciprocation ofthe reciprocatory member to rockthe pawlA carrier in either direction from its normal position offrestto reverse the direction of rotation of the Work support; a normallyidle clutch between the power drive and the` work support rotatingmeans;

means to engageand disengage said clutch to effect intermittent advancesof the work support from said normal or starting position; and means torestore the work support and work to` their normalv intermediatepositions at sometime during the periods of disconnection-of the clutch.

13. A shoe tacking machineincluding a rotatable vvork support; an edgerest against which the work on the support is pressed during rotation ofthe support; a power drive; means operable byv the power drive topositively rotate the work support and work, first in one direction andlater in the opposite direction from. a normal intermediate or startingposition in each instance; means to restore the work support and workafter their advance in either of said directions by the power drive; aclutch betweenthe power drive and the work support rotating mechanism;control means to intermittently open and close the clutch; and inormally idle'means operable byr said control means to preventrestoration of the worktsupport and work to their normal positions. j

l14. A shoe tacking machine including arotatable work support; an edgerest against which the work on the work support is. held during rotationof the support; a power drive; means operable by the power drive -topositively and intermittently rotate the Work support and work in onedirection and then in the opposite direction .from the normalintermediate orstarting position of the Work support;,means to controlthe direction in which the lWork support shall rst rotate ;l a clutchbetween the power drive and the work l support rotating means; clutchengaging and disltion .until the means controlling the direction ofrotation is restored to its normal idle position.

l5. A shoe tacking machine including a rotatable work support; an edgerest against which the Work on the work support is held during rotationof the support; apower drive; means operable by the power drive topositively rotate the work support and work, rst in one direction andlater in the opposite direction from the normal intermediate or startingposition of the work support; a clutch between the power drive and thework support rotating means; intermittently operated means to render theclutch effective or ineffective alternately; means to control thedirection of rotation of the work support from its normal intermediateor starting position; and spring motormeans tensioned by the worksupport rotating means when rotating the support in either direction, torestore the work support and work to their normal starting positionsafter every advance of said work support and work from its normalstarting position and during the time said clutch is ineiective.

16. A shoe tacking machine, including a rotatable work support; an edgerest against which the work on the work support is held during rotationof the support; a power drive; means operable by the power drive torotate the work support and work, first in one direction, and then afteran l interval, in the opposite direction from the normal intermediate orstarting position of the work support in each instance; a clutch betweenthe power drive and the work support rotating means; means, theoperation of which is co-ordinated with the operation of the worksupport rotating means, to engage and disengage said clutch and tocontrol the direction of rotation of the work support; means to restorethe work support and work to the normal intermediate or startingposition after each advance rotation of the work support and during theperiods of disengagement of the clutch; and automaticallyoperable meansto restrain the work support against return to normal starting positionafter each advance until after the clutch is disengaged.

1'7. A shoe tacking machine, including a rotatable work support; an edgerest against which the work on the work support is held during rotationof the support; a power drive; means operable by the power drive torotate the work support and work. rst in one direction, and then afteran interval. in the opposite direction from the normal intermediate orstarting position of the work support in each instance; a clutch betweenthe power drive and the work support rotating means; a transmittinglever normally lying intermediate its limits of travel; a cam to rocksaid lever first in one direction and then in theother from and to itsnormal intermediate position; a clutch control member; a bellcrankrockingwith said transmitting lever; and slotted links to connect theopposite arms of the bellcrank with the clutch control member to actuatethe clutch control member in one and the same direction irrespective ofthe direction of movement of the bellcrank.

18. A shoe tacking machine, including a rotatable work support; an edgerest against which the work on the work support is held during rotationof the support; a power drive; means operable by the power drive torotate the work support and work, first in one direction,- and thenafter an interval, in the opposite direction from the normalintermediate or starting position of the work support in each instance;a clutch between the power drive and the work support rotating means; atransmitting lever normally lying intermediate its limits of travel; acam to rock said lever first in one direction and then in the other fromand to its normal intermediate psition; a clutch control member; apivotally supported manually operable emergency lever to which one endof the clutch control member is pivotally connected; a bellcrank rockingwith said transmitting lever; and slotted links connecting therespective arms of the bellcrank with the clutch control memberintermediate its ends, to actuate the clutch control member on itsconnection with the emergency lever as a fulcrum whenever thetransmitting lever is rocked to either limit or its movement, to engagethe clutch, said connection of the slotted links with the clutch controlmember constituting the fulcrum about which said clutch control memberrocks, upon actuation of the emergency lever to shift said clutchcontrol member in the opposite direction and disengage the clutch.

19. A shoe tacking machine including a rotatable work support; an edgerest against which the work on the work support is held during rotationof the work support; a power drive; normally idle means operable by thepower drive to rotate the work support and work, first in one directionand later in the opposite direction from the normal intermediate orstarting position of the work support in each instance; selective meansto determine the direction in which the work support shall first rotatefrom its normal starting position and to automatically condition thework support rotating means to rotate the work support successively inopposite directions from its normal starting position; means undercontrol of the selective means to retain the Work support at each limitof its advance travel; and means to restore the work support and work toits normal starting position upon the release oj the retaining means.

20. In a shoe tacking machine, the combination with a continuouslyoperating driving member; an edge rest; and a work holder shiftabletowards and from the edge rest, and rotatable while the work is incontact with the edge rest; of means operable by the driving member torotate the work holder from an intermediate or normal starting position,rst in one direction with a smooth uninterrupted movement, and later inthe opposite direction; control means to determine the direction inwhich the work holder shall rotate; clutch means controlled by thecontrol means to connect and disconnect the drive member and the workholder rotating means; coupling means controlled by the means whichrotates the work holder, to alternately connect and disconnect thecontrol means and the driving member; and means connected with the meanswhich rotates the work holder, for restoring the work holder and work tostarting position during each disconnection of the driving member andwork holder rotating means.

21. In a shoe tacking machine, the combination with a continuouslyoperable drive member; an edge rest; and an axially rotatable workholder shiftable towards and from the edge rest; of means toautomatically oscillate the work holder, when in contact with the edgerest, rst in one direction from and to its normal intermediate orstarting position, and then in the opposite direction from and to itsnormal intermediate or starting position by successive movements,effected by mechanisms, the successive and repeated and alternatingoperations of which are dependent upon each other, comprising a controlmechanism, a Work rotating mechanism for positively advancing the workin one direction and in the other from its normal intermediate4

